US10844905B2 - Planetary transmission - Google Patents

Planetary transmission Download PDF

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US10844905B2
US10844905B2 US16/330,248 US201716330248A US10844905B2 US 10844905 B2 US10844905 B2 US 10844905B2 US 201716330248 A US201716330248 A US 201716330248A US 10844905 B2 US10844905 B2 US 10844905B2
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planetary
planetary gear
transmission
bearing
lubrication
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US20190203768A1 (en
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Thomas Meyer
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Flender GmbH
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Flender GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F16C33/1055—Details of supply of the liquid to the bearing from radial inside, e.g. via a passage through the shaft and/or inner sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/02—Sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0486—Gearings with gears having orbital motion with fixed gear ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/40—Transmission of power
    • F05D2260/403—Transmission of power through the shape of the drive components
    • F05D2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05D2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclical, planetary or differential type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/98—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction
    • Y02E10/722—

Definitions

  • the present invention relates planetary transmissions and, more particularly, to a planetary transmission for a wind turbine, comprising a transmission housing, a central sun gear that is retained in the transmission housing such that it can rotate about a central transmission rotational axis and that has an outer toothing, a ring gear that is arranged concentrically in relation to the central transmission rotational axis in the transmission housing and which has an inner toothing, a planetary carrier that is mounted in the transmission housing such that it can rotate about a central transmission rotational axis and multiple planetary gears that are mounted on the planetary carrier via a planetary gear housing configured as a sliding bearing such that they can rotate about planetary gear rotational axes and that have outer toothings that engage with the inner toothing of the ring gear and the outer toothing of the sun gear.
  • Planetary transmissions serve, for example, as transmissions for converting a low rotational speed of a drive shaft of the planetary transmission into a much higher speed of a take-off shaft of the planetary transmission. Accordingly, planetary transmissions are frequently built into wind turbines, where a low speed of the rotor shaft is converted into a far higher speed of the generator shaft. When used in wind turbines, because of the variable wind conditions, planetary transmissions are operated under widely changing operating conditions. As a result of occasionally extremely low rotational speeds of the drive shaft and at the same time extremely high forces acting on the bearings, roller bearings for bearing support of the planetary gears can be built into planetary transmissions for wind turbines.
  • planetary gear bearings for wind turbines can also be embodied as sliding bearings.
  • a planetary transmission for a wind turbine is described in EP 2 383 480 A1, for example, and has a transmission housing in which a central sun gear with outer toothing is retained so that it can rotate about a central transmission axis.
  • a ring gear with inner toothing is provided in the transmission housing concentric to the central rotational axis of the transmission.
  • a planetary carrier is likewise supported in a transmission housing to allow its rotation about the central rotational axis of the transmission.
  • Retained on the planetary carrier are a number of planetary gears.
  • the planetary gears have outer toothing that engages with the inner toothing of the ring gear and the outer toothing of the sun gear.
  • the planetary gears are rotatably supported on the planetary gear bearings formed as radial sliding bearings.
  • its bearing play must also take into consideration that temperature-dependent and/or load-dependent expansions and/or deformations can occur during the operation of the radial sliding bearing. Therefore, the components of the radial sliding bearing and/or the running surfaces of the supported planetary gears must be manufactured with high precision, i.e., with low production tolerances and/or must be reworked during installation, which is associated with high costs.
  • Radial sliding bearings can exclusively dissipate radial forces.
  • supplementary axial sliding bearings which dissipate axial forces acting on the planetary gears, are necessary.
  • Such axial sliding bearings can be formed in the contact area between flanges of the planetary carrier and end face sides of the planetary gears, for example, and likewise increase the costs of such planetary gear bearings.
  • It is an object of the present invention is to provide a planetary transmission, which corresponds in particular to that stated at the outset, which makes a simple structure possible, exhibits little wear and/or is easy to handle, where the bearing play of sliding bearings particularly employed is easy to set.
  • a planetary transmission particularly for a wind turbine, with a transmission housing that comprises a central sun gear that is retained in the transmission housing such that it can rotate about a central transmission rotational axis in the transmission housing and bears outer toothing, and a ring gear that is arranged concentrically to the central transmission rotational axis and has inner toothing.
  • the planetary transmission particularly has a one-sided planetary carrier, which is mounted in the transmission housing such that it can rotate about the central transmission rotational axis, and multiple planetary gears that are mounted on the planet carrier via a planetary gear housing configured as a sliding bearing such that they can rotate about planetary gear rotational axes and that have outer toothings that engage with the inner toothing of the ring gear and the outer toothing of the sun gear.
  • the one-sided planetary carrier has only one flange compared to the two-sided planetary carrier.
  • the two-sided planetary carrier has flanges on both sides of the planetary gears arranged in one plane, which carry or guide the planetary gears.
  • the planetary gear shaft is only carried via precisely one carrier on precisely one end face side of the planetary gear. This applies especially to all planetary gears of the planetary transmission.
  • the planetary gear is only retained via this one planetary carrier.
  • the planetary gear is only supported on one shaft, in particular the drive shaft or the take-off shaft of the transmission.
  • the planetary gears are only retained by one carrier on only one end face side of the planetary gears.
  • Each planetary gear bearing has two annular bearing bodies, where at least one of the annular bearing bodies is penetrated by a planetary gear shaft and is rotationally fixed on same, where conical sliding surfaces are formed on the outer circumferential surfaces of the bearing bodies such that the tapered ends of the bearing bodies point towards one another, and where running surfaces corresponding to the sliding surfaces of the planetary gear bearing are formed on the inner circumferential surfaces of the planetary gear.
  • a conical planetary sliding bearing can be realized in one-sided and also in two-sided planetary carriers. In a two-sided planetary carrier, this can result in a stress. Thus, it can be that the planetary gear shaft flexes between its clamping points in the flanges.
  • This deformation is to be compensated for or prevented by reinforcements, and also by a torsion of the two-sided planetary carrier being skewed in relation to the two central toothed wheels ring gear and sun gear. This can lead within the tooth engagements to an uneven width load distribution.
  • the transmission has a first end face side and a second end face side, where the one-sided planetary carrier is in the area of only one end face side, in particular the first end face side, and where the at least one annular bearing body, which is penetrated by the planetary gear shaft and is fixed rotationally on said shaft, is decoupled on the second end face side from a further planetary gear.
  • the decoupling is particularly produced by it not having a second flange, which serves as a mirror-image flange for carrying a plurality of planetary gears.
  • each planetary gear carrier in the planetary transmission has two annular bearing bodies, which are penetrated by a planetary gear shaft and fixed rotationally on the shaft and on the outer circumferential surfaces of which conical sliding surfaces are embodied, then these can be formed so that it is possible to easily set the bearing play of the sliding bearing used and to achieve a simple structure.
  • This is based on the consideration of using axially divided double sliding cone bearings, which are capable of dissipating both axial and also radial forces.
  • the opposing arrangement of the two conical sliding surfaces means that a planetary gear can be defined both in the axial direction and also in the radial direction.
  • the radial bearing play can be set in a simple manner.
  • the torsion proofing of the bearing bodies can be brought about, for example, by bearing bodies produced with excess dimension being shrunk onto the planetary gear shaft after they have been positioned.
  • a latching of at least one bearing body on the planetary gear shaft occurs, in order to latch the at least one bearing body.
  • the at least one bearing body is fixed axially on the planetary gear shaft by the latching.
  • the planetary gear shaft is a flex pin with a hollow cylinder.
  • the hollow cylinder carries at least one of the bearing bodies.
  • the flex pin has a lubricant line.
  • the lubricant line is also routed in particular through the hollow cylinder, so that lubricant can enter the sliding bearing and get between the sliding/running surfaces.
  • a lubrication gap is provided between the sliding surfaces of the planetary gear carrier and the corresponding running surfaces of the supported planetary gear, where a first of these lubrication gaps is different from the second of these lubrication gaps.
  • a first lubrication gap and a second lubrication gap have a different axial length. Influence can be exerted on the load distribution in this way, for example.
  • At least one of the lubrication gaps has axially different heights.
  • the transport of the lubricant can be influenced in this way, for example.
  • the first lubrication gap is at a different angle to the rotational axis of the planetary gear than the second lubrication gap.
  • the distribution of forces in the bearing can be influenced in this way.
  • At least one bearing body is adjustable in the axial direction, in order to set a lubrication gap of defined height between the sliding surfaces of the supported planetary gear carrier and the corresponding running surfaces.
  • An optimum height of the lubrication gap between the sliding surfaces of the supported planetary gear carrier and the corresponding running surfaces is an important precondition for reliable operation of the planetary transmission.
  • one bearing body is adjustable, while the other bearing body has an axially fixed position.
  • the bearing body with the axially fixed position can serve as a reference for adjusting the adjustable bearing body, which is compatible with a simple and precise setting of the optimum height of the lubrication gap of the planetary gear carrier.
  • the axial position of the axially fixed bearing body can be defined by an axial stop.
  • a flange of the planetary gear carrier or a radial annular shoulder formed on the planetary gear axis can serve in particular as an axial stop.
  • an adjuster for axial adjustment is assigned to the adjustable bearing body.
  • Such an adjuster simplifies the setting and in particular also the convenient subsequent adjustment of the inventive planetary transmission as part of maintenance, if the height of the lubrication gap of the sliding body has changed through wear.
  • distance elements are provided as the adjuster, which are arranged between a bearing body and the neighboring flange of the planetary carrier and/or between the bearing bodies.
  • the adjustable bearing body is screwed onto the planetary gear shaft.
  • an inner thread is formed on the adjustable bearing body and a corresponding outer thread is embodied on the planetary gear shaft.
  • the adjustable bearing body can be screwed into a neighboring flange of the planetary gear carrier.
  • an outer thread is formed on the adjustable bearing body and a corresponding inner thread is formed in the neighboring flange of the planetary gear carrier.
  • torsion proofing can be provided, via which the bearing body screwed into the planetary gear carrier or the flange can be fixed. Torsion proofing also allows a secure fixing of the set axial position of the adjustable bearing body. Rings on the shaft of which the outer dimension is larger than the holes in the planetary gear carrier can be used with the bearings described, the shaft does not have to be designed with steps.
  • a combination of a number of different adjusters is also possible for setting the optimum height of the lubrication gap of the planetary gear bearing.
  • the at least one lubrication pocket is formed in each sliding surface, into which a lubricant channel opens out, which penetrates the bearing body radially, where the lubricant channel is connected to an eccentric lubricant feed channel, which is formed in the planetary gear shaft and axially penetrates the shaft.
  • lubricant will be supplied to the sliding surfaces of the planetary gear bearing as part of a pressurized lubrication.
  • the lubricant is introduced under pressure into the eccentric lubricant feed channel and flows from there through lubricant channels into the lubricant pockets, from where it is distributed onto the sliding surfaces.
  • a distance ring is formed between the bearing bodies, which surrounds the planetary gear shaft and defines a minimum axial distance between the bearing bodies. Such a distance ring can prevent the axial distance and thus the height of the lubrication gap being set too small, which is an obstacle to the planetary gear running with as little wear as possible.
  • a lubricant collection groove can be formed on an inner circumferential surface of the distance ring. This lubricant collection groove can be used for distribution of lubricant between the bearing bodies.
  • a plurality of lubricant channels which open out into the lubricant collection groove are formed in the distance ring. These lubricant channels enable lubricant to flow out of the lubricant collection groove in the direction of the lubrication gap.
  • a lubricant feed channel which opens out radially into the lubricant collection groove of the distance ring is formed in the planetary gear shaft.
  • a lubricant feed channel allows lubricant to be supplied to the lubricant collection groove in the distance ring in the form of centrifugal lubrication. Centrifugal lubrication makes it possible to continue to operate the planetary transmission in an emergency mode if the pressure lubrication fails.
  • FIG. 1 shows a schematic axial cross-sectional view of a planetary transmission in accordance with a first embodiment
  • FIG. 2 shows an axial overhead view of a planetary carrier of the planetary transmission shown in FIG. 1 , along the line II-II;
  • FIG. 3 shows an axial cross-sectional view of a planetary gear carrier of the planetary transmission shown in FIG. 1 ,
  • FIG. 4 shows a perspective side view of a bearing body of the planetary transmission shown in FIG. 1 ;
  • FIG. 5 shows a section of a cross-sectional view of a planetary gear carrier in accordance with the invention
  • FIG. 6 shows a section of a cross-sectional view of a planetary gear carrier with a hybrid bearing body in accordance with the invention
  • FIG. 7 shows an axial cross-sectional view of a planetary gear carrier in accordance with a second embodiment of the present invention.
  • FIG. 8 shows an axial cross-sectional view of a planetary gear carrier in accordance with a third embodiment of the present invention.
  • FIG. 9 shows an axial cross-sectional view of a planetary gear carrier in accordance with a fourth embodiment of the present invention.
  • FIG. 10 shows a section of a cross-sectional view of a planetary gear carrier with a flex pin in accordance with the invention
  • FIG. 11 shows a section of a cross-sectional view of a planetary gear carrier with a shortened flex pin in accordance with the invention
  • FIG. 12 shows a flex pin with a lubricant line in accordance with the invention
  • FIG. 13 shows a section of a cross-sectional view of a planetary gear carrier with asymmetrical bearing bodies in accordance with the invention.
  • FIG. 14 shows a section of a cross-sectional view of a planetary gear carrier with a lubrication gap of different height in accordance with the invention.
  • FIGS. 1 to 4 show a planetary transmission 1 in accordance with a first embodiment of the present invention.
  • the planetary transmission 1 has a transmission housing 2 , which is penetrated on opposing end face sides by a drive shaft 3 and a take-off shaft 4 respectively.
  • a central sun gear 5 with an outer toothing 6 is retained rotatably on the take-off shaft 4 about the central transmission rotational axis 37 .
  • a ring gear 7 with an inner toothing 8 concentric to the central transmission rotational axis 37 , which has a fixed connection to the transmission housing 2 and surrounds the sun gear 5 .
  • a planetary carrier 9 is retained rotatably about the central transmission rotational axis 37 in the transmission housing 2 on the drive shaft 3 .
  • the planetary carrier 9 has a flange 9 on a first end face side of the planetary transmission 1 or the planetary gears 13 . There is no further flange located on the second end face side 32 of the planetary transmission 1 or the planetary gears 13 .
  • the flange 9 carries the planetary gears.
  • the planetary carrier 9 is configured such that the carrier only has one flange 9 on the drive shaft 3 side.
  • the two flanges are then connected to one another via planetary gear shafts.
  • the planetary gears are arranged between these two flanges of the planetary carrier. This is not shown in FIG. 1 , however.
  • the setting of the bearing play of the sliding cone bearings for the two-sided planetary carrier is complex, at the same time the components must be secured on the shaft to prevent them from turning. This is made difficult by the two-sided planetary carrier and the form fit of the sliding cone bearings, because the shaft is introduced axially as the last component into the subassembly of the carrier. Accordingly, no radial torsion proofing of the components on the shaft can be realized in this way.
  • the planetary transmission 1 of FIG. 1 only has one flange.
  • the planetary carrier 9 can also carry a number of planetary gear shafts other than three.
  • a planetary gear bearing 12 formed as a sliding bearing, in which a planetary gear 13 is rotatably supported about a planetary gear rotational axis 36 .
  • the planetary gears 13 have external toothings 14 , which engage with the inner toothing 8 of the ring gear 7 and the outer toothing 6 of the sun gear 5 .
  • the planetary gear bearing 12 has a first bearing body 12 a and a second bearing body 12 b.
  • the planetary gear rotational axis 36 is only connected to the planetary carrier 9 on one side.
  • a free end of the planetary gear rotational axis 36 is produced in relation to clamping.
  • This subassembly can now be mounted via an axial slide-in assembly. In this way, even a form fit of the conical sliding bearing cannot present any problem.
  • the bearing body 12 a (this can also be referred to as a sliding bearing ring) can be secured radially on the shaft against rotation.
  • the planetary gear is then mounted axially over the free end of the planetary gear rotational axis 36 , before the further bearing body 12 b is put on axially.
  • Each planetary gear carrier 12 has two annular bearing bodies 12 a and 12 b , which are penetrated by the planetary gear shaft 11 and are held on the shaft in a torsion-proof manner.
  • Bevels or the like can be provided in axial edge areas of the sliding surfaces 16 , in order to counteract edges being formed as a result of wear.
  • Each bearing body 12 a , 12 b is penetrated radially by a lubricant channel 17 .
  • the lubricant channel 17 is connected to an eccentric lubricant feed channel 18 , which penetrates the planetary gear shaft 11 axially.
  • the lubricant channel 17 opens out into a lubrication pocket 19 , which is formed in an area of the sliding surface 16 of the bearing body 12 a , 12 b subject to little load as a flattening-off or a recess.
  • the sliding surfaces 16 are supplied with lubricant in the form of a pressure lubrication during regular operation of the planetary gear bearing 12 .
  • the tapered ends of the bearing bodies 12 a , 12 b point towards each other, where running surfaces 20 corresponding to the sliding surfaces 16 of the planetary gear bearing 12 are formed on the inner circumferential surfaces of the planetary gear 13 .
  • a distance ring 21 Arranged between the bearing bodies 12 a , 12 b of the planetary gear bearing 12 is a distance ring 21 , which surrounds the planetary gear shaft 11 and defines a minimum distance between the bearing bodies 12 a , 12 b .
  • Formed on the inner circumferential surface of the distance ring 21 is an annular lubricant collection groove 22 , into which a plurality of lubricant channels 23 penetrating the distance ring open out.
  • a central lubricant feed channel 24 Corresponding to the lubricant collection groove 22 of the distance ring 21 , a central lubricant feed channel 24 , which opens out into the lubricant collection groove 22 of the distance ring 21 is formed in the planetary gear shaft 11 .
  • the lubricant collection groove 22 and the plurality of lubricant channels 23 there can be a centrifugal lubrication of the planetary gear bearing 12 , which is sufficient for an emergency operating mode of the planetary gear.
  • the axial widths b 1 and b 2 of the bearing bodies 12 a and 12 b and the width b 3 of the distance ring 21 fulfill the relationship b 1 +b 2 +b 3 >B, where B refers to the desired width of the planetary gear bearing 12 .
  • B refers to the desired width of the planetary gear bearing 12 .
  • the axial determination is also produced by the retaining ring 30 , through which the width B is predetermined.
  • ⁇ S ⁇ b sin( ⁇ ) between a change in height ⁇ S of the lubrication gap 25 and an axial adjustment of the respective bearing body 12 a or 12 b brought about by change in width ⁇ b.
  • FIG. 5 shows a section of a cross-sectional view of a planetary gear bearing, in which the retaining ring 30 is screwed to the planetary gear shaft 11 via a thread 33 .
  • the bearing bodies 12 a and 12 b with the distance ring 21 lying between them are pressed onto the planetary carrier 9 via the retaining ring 30 . Consequently, there is a set sliding support in an X arrangement for the planetary gear bearing with a one-sided planetary carrier 9 .
  • FIG. 6 shows a section of a cross-sectional view of a planetary gear bearing with a hybrid bearing body 9 a . If the hybrid bearing body 9 a from FIG. 6 is compared with elements from FIG. 5 , for example, then it becomes clear that the hybrid bearing body 9 a integrates the functions of the elements planetary carrier 9 , bearing body 12 a and planetary gear shaft 11 of FIG. 5 into one component 9 a . This reduces the complexity and can increase the stiffness of the transmission.
  • FIG. 7 shows a planetary gear bearing 12 of a planetary transmission 1 according to a further embodiment of the planetary transmission. Inserted between the bearing body 12 a and the distance ring 21 and also between the bearing bodies 12 a , 12 b and the neighboring elements in each case, such as planetary carrier 9 or retaining ring 30 , are distance elements 26 .
  • the axial widths b 1 , b 2 and b 3 of the bearing bodies 12 a , 12 b and of the distance ring 21 , on the one hand, as well as D 1 , D 2 and D 3 of the distance elements 26 , on the other hand, fulfill the relationship b 1 +b 2 +b 3 +D 1 +D 2 +D 3 B, so that the bearing bodies 12 a , 12 b , the distance ring 26 and the distance elements 26 are fixed axially in their position.
  • the bearing bodies 12 a and 12 b and the distance ring 21 initially fulfill the relationship b 1 +b 2 +b 3 ⁇ B in order to set the desired height S of the lubrication gap 25 .
  • b 1 +b 2 +b 3 and B are defined as in the embodiment shown in FIG. 3
  • D 1 +D 2 +D 3 refer to the axial widths of the distance elements 26 .
  • the axial widths of the bearing bodies 12 a and 12 b and the distance ring 21 fulfill the relationship b 1 +b 2 +b 3 ⁇ B.
  • distance elements 26 of suitable thicknesses D 1 +D 2 +D 3 are inserted at the points such that the sum of the current thicknesses D 1 +D 2 +D 3 of all inserted distance elements 26 is equal to the difference between the bearing width B and the sum of the axial widths b 1 +b 2 +b 3 of the bearing bodies 12 a and 12 b and the distance ring 21 and the lubrication gap S possesses the required height S.
  • FIG. 8 shows, in a section, a planetary gear bearing 12 of a planetary transmission 1 in accordance with a further embodiment.
  • the adjustable bearing body 12 a is screwed onto the planetary gear shaft 11 .
  • an inner thread is formed on the adjustable bearing body 12 a and a corresponding outer thread on the planetary gear shaft 11 .
  • This screw connection 27 allows a stepless adjustment of the axial position of the adjustable bearing body 12 a on the planetary gear shaft 11 .
  • the axially fixed bearing body 12 b is screwed to a bearing body holder 10 with a screw 39 .
  • the bearing body holder 10 is axially fixed via a retaining ring 30 , which projects into the planetary gear shaft 11 and into the bearing body holder 10 .
  • the bearing body 12 a is fixed by a torsion proofing 28 in the corresponding axial position. Pins, bolts or the like can be used as the torsion proofing 28 . If the height S of the lubrication gap 25 changes over the course of time because of operation-related wear, the adjustable bearing body 12 a is able to be re-adjusted appropriately, in order to restore the required height S of the lubrication gap 25 .
  • the diagram depicted in FIG. 9 shows a planetary gear bearing 12 of a planetary transmission 1 in accordance with a further embodiment.
  • the adjustable bearing body 12 b is screwed via a thread 27 to the planetary gear shaft 11 and secured via a torsion proofing 28 .
  • the screw connection 27 makes it possible to position the bearing body 12 b in the axial direction.
  • pins, bolts or the like can be used as the torsion proofing 28 .
  • the axial position of the axially fixed bearing body 12 a is fixed by a radial ring shoulder 29 serving as an axial stop formed on the planetary gear shaft 11 .
  • the required height S of the lubrication gap 25 can be set. If the height S of the lubrication gap 25 of the planetary gear bearing 12 has shifted as a consequence of operation-related wear, then the planetary gear bearing 12 can be readjusted by axial adjustment of the bearing body 12 b.
  • the proposed methods and embodiments for setting an optimum height of the lubrication gap 25 of the planetary gear bearing 12 can be combined with one another.
  • the planetary carrier 9 is set in rotation by the drive shaft 3 .
  • the planetary gears 13 roll along the inner side of the ring gear 7 .
  • the take-off shaft 4 turns at a higher rotational speed than the drive shaft 3 , because the planetary gears 13 have a smaller circumference than the planetary gear axes of rotation 36 describe in their rotation about the central transmission rotational axis 37 of the planetary transmission 1 .
  • the bearing is continuously supplied with lubricant by the central lubricant feed channel 24 .
  • the lubricant is initially distributed in the lubricant collection groove 22 of the distance ring 21 and then flows through the at least one lubricant channel 23 in the direction of the lubrication gap 25 (see FIG. 3 ).
  • One advantage of the described planetary transmission 1 lies in the fact that, unlike cylindrical sliding bearings, no additional axial sliding bearing has to be provided in order to fix the planetary gear 13 in the axial direction. This accordingly makes the processing for formation of additional axial sliding surfaces superfluous.
  • a further advantage of the described sliding bearing lies in the simple adjustment or readjustment of the height S of the lubrication gap 25 , which allows a greater component tolerance in the manufacturing of the components needed for the planetary gear bearings. Overall cost benefits from lower manufacturing costs and an increased lifetime of the planetary gear bearing 12 as a result of the re-adjustment options can be achieved in the use of such a planetary transmission.
  • the diagram depicted in FIG. 10 shows a section of a cross-section of a planetary gear bearing with a flex pin 34 , a conical sliding bearing with classical flex pin.
  • the flex pin 34 carries a hollow cylinder 35 .
  • the hollow cylinder 35 carries the bearing bodies 12 a and 12 b , as well as the distance ring 21 .
  • a groove channel 43 is formed via the distance ring 21 .
  • the bearing body 12 a is positioned axially via a stop 40 .
  • the retaining ring 30 clamps in the bearing bodies 12 a and 12 b , as well as the distance ring 21 .
  • FIG. 11 shows a section of a cross-section of a planetary gear bearing with a shortened flex pin 34 .
  • the flex pin 34 ends, compared to the flex pin depicted in FIG. 10 , in an axially central area of the hollow cylinder 35 .
  • the flex pin 34 is offset relative to the middle 42 of the planetary gear 13 by the offset 41 . In this way, a symmetrical distribution of force can be achieved.
  • the lower mass of the flex pin 34 depicted in FIG. 11 also reduces the inertia.
  • the diagram depicted in FIG. 12 shows a flex pin 34 as a shaft for the planetary gear with an integrated lubricant line 38 .
  • the lubricant line 38 (e.g., for supplying an oil) also penetrates the hollow cylinder 35 and opens out into the groove channel 43 .
  • the lubricant line 38 is offset relative to the end piece 44 of the flex pin 34 .
  • An offset 41 a and 41 b relative to the middle 42 of the planetary gear is produced.
  • the offset 41 a and the offset 41 b are different.
  • the end piece 44 completely covers the groove channel 42 .
  • the gimbal joint with the hollow cylinder (sleeve) can be adapted and set via the offset 41 (see FIG. 11 ) of the connection of the shaft (flex pin) to the hollow cylinder (flex pin sleeve), depending on the degree of deformation.
  • the diagram depicted in FIG. 13 shows a section of a cross-section of a planetary gear bearing with asymmetrical bearing bodies 12 a and 12 b .
  • the bearing body 12 a with its shaft length b 1 , has a different shaft length from the bearing body 12 b (with the shaft length b 2 ).
  • the groove channel 43 is offset relative to the middle 42 of the planetary gear by the offset 41 .
  • the first lubrication gap 25 a makes a first angle ⁇ 1 with the planetary gear shaft 36 .
  • the second lubrication gap 25 b makes a second angle ⁇ 2 with the planetary gear shaft 36 .
  • the cone angles ⁇ 1 and ⁇ 2 can be different for the two sliding cone bearings.
  • the left-hand sliding bearing with the bearing body 12 a is set larger than the right-hand sliding bearing with the bearing body 12 b . This can likewise serve as a setting option, in order to compensate for asymmetrical deformations resulting from uneven loading.
  • the diagram depicted in FIG. 14 shows a section of a cross-section of a planetary gear bearing with a lubrication gap of different height 45 a and 45 b .
  • the first lubrication gap 25 a has a height 45 a increasing from inside to outside.
  • the second lubrication gap 25 b has a height 45 b increasing from inside to outside.
  • the minimum heights of the lubrication gaps 25 a and 25 b are the same.
  • the maximum heights of the lubrication gaps 25 a and 25 b are different. This produces asymmetrical sliding cone bearings with angular correction.
  • the cone angles of the respective cone bearing functional surfaces are formed differently. This can be done as a geometrical correction of the sliding bearings when the deformations are correspondingly large.

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10989119B2 (en) * 2018-11-23 2021-04-27 Safran Transmission Systems Planet-carrier for a mechanical reduction gear of an aircraft turbine engine
US11339869B2 (en) * 2018-11-23 2022-05-24 Safran Transmission Systems Lubricating and cooling core for a mechanical reduction gear of an aircraft turbine engine
US11644013B2 (en) 2019-05-21 2023-05-09 Miba Gleitlager Austria Gmbh Nacelle for a wind turbine

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT519288B1 (de) * 2016-10-21 2018-07-15 Miba Gleitlager Austria Gmbh Lagerelement
DE102017222901A1 (de) * 2017-12-15 2019-06-19 Zf Friedrichshafen Ag Planetengetriebestufe mit einer Gleitlageranordnung, insbesondere für eine Planetenradlagerung in einem Windkraftgetriebe
US10683773B2 (en) * 2018-05-25 2020-06-16 Pratt & Whitney Canada Corp. Planetary gearbox having compliant journal bearings
DE102018214083A1 (de) * 2018-08-21 2020-02-27 Zf Friedrichshafen Ag Planetengetriebe für eine Windkraftanlage
DK3670967T3 (da) * 2018-12-17 2021-10-11 Moventas Gears Oy Planethjulaksel til et planetgear
CN110611168B (zh) * 2019-09-21 2020-11-20 深圳市锦凌电子有限公司 一种5g通信的多天线校准装置
DK3798470T3 (da) * 2019-09-27 2023-06-12 Flender Gmbh Planetgear med forbedret smøremiddelforsyning, drivlinje og vindkraftanlæg
US11149786B2 (en) 2020-02-28 2021-10-19 Pratt & Whitney Canada Corp. Carrier journal with anti-rotation feature
CN111828558B (zh) * 2020-08-10 2022-09-20 重庆大学 一种可调隙少齿差减速器
EP4047228A1 (de) * 2021-02-23 2022-08-24 Flender GmbH Lageranordnung, generatorgetriebe, windkraftanlage und computerprogrammprodukt
GB202103169D0 (en) * 2021-03-08 2021-04-21 Rolls Royce Plc Planetary gearbox
US11542842B2 (en) * 2021-05-24 2023-01-03 Borgwarner Inc. Electrically-actuated camshaft phasers with tapered features
DE102021122300A1 (de) * 2021-08-27 2023-03-02 Rolls-Royce Deutschland Ltd & Co Kg Planetengetriebe
CN114877033B (zh) * 2022-06-07 2023-09-15 南高齿(淮安)高速齿轮制造有限公司 一种传动机构

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020114549A1 (en) * 2001-02-21 2002-08-22 Kazuo Hokkirigawa Special type bearing device
US20080315697A1 (en) * 2007-06-21 2008-12-25 Laurent Bonnet Gear integrated generator for wind turbine
US7662059B2 (en) 2006-10-18 2010-02-16 United Technologies Corporation Lubrication of windmilling journal bearings
EP2383480A1 (de) 2010-04-30 2011-11-02 Winergy AG Planetengetriebe für eine Windkraftanlage
US8246503B2 (en) 2009-06-10 2012-08-21 United Technologies Corporation Epicyclic gear system with improved lubrication system
US8636615B2 (en) 2010-08-31 2014-01-28 Mitsubishi Heavy Industries, Co., Ltd Planetary gear train with oiling system for supplying lubricant oil to bearing of planetary gear and wind turbine generator incorporating the same
US20150125104A1 (en) * 2013-11-07 2015-05-07 Aktiebolaget Skf Bearing arrangement for fluid machinery application
DE102014205980A1 (de) 2014-03-31 2015-10-01 Schaeffler Technologies AG & Co. KG Planetentrieb mit einem Planetenrad, das mittels zwei Planetenbolzen in einem Planetenträger gelagert ist
DE102014214331A1 (de) 2014-07-23 2016-01-28 Schaeffler Technologies AG & Co. KG Planetengetriebe
EP3091255A1 (de) 2015-05-07 2016-11-09 Siemens Aktiengesellschaft Planetengetriebe
US20180347623A1 (en) * 2015-10-29 2018-12-06 Ntn Corporation Method for producing bearing ring, double row tapered roller bearing, and method for producing double row tapered roller bearing

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR915604A (fr) 1944-09-11 1946-11-13 Perfectionnements apportés aux paliers ou coussinets
US2721773A (en) 1953-05-11 1955-10-25 Jr Vincent Gentile Slip sleeve bearing
GB1101131A (en) 1964-02-07 1968-01-31 Nat Res Dev Improvements relating to gears
US3476451A (en) 1966-02-07 1969-11-04 Everett H Schwartzman Fluid bearing system
US3984152A (en) 1970-11-13 1976-10-05 Haines Charles E Frusto-conical laminar bearings
GB1407405A (en) 1971-10-08 1975-09-24 Vandervell Products Ltd Housing and shaft assembly
GB1451045A (en) 1972-08-22 1976-09-29 Cam Gears Ltd Rack and pinion assemblies
DE7826851U1 (de) 1978-09-09 1979-01-04 Fichtel & Sachs Ag, 8720 Schweinfurt Freilaufnabe mit ruecktrittbremse
US5455778A (en) 1987-05-29 1995-10-03 Ide; Russell D. Bearing design analysis apparatus and method
DE19534791C2 (de) * 1995-09-20 1997-11-13 Ford Werke Ag Planetenradträgeranordnung mit Axialabstützung
GB0002126D0 (en) * 2000-01-31 2000-03-22 Hanson Transmissions Internati Planetary gear stage
DE10064815A1 (de) * 2000-12-22 2002-07-11 Zahnradfabrik Friedrichshafen Planetengetriebe
JP2006170413A (ja) * 2004-12-20 2006-06-29 Seisa Gear Ltd はすば遊星減速機の軸受装置
GB0518026D0 (en) 2005-09-06 2005-10-12 Orbital 2 Ltd A gear
WO2009141140A2 (de) 2008-05-20 2009-11-26 Urs Giger Windkraftanlage, getriebe für eine windkraftanlage und flexpin
EP2304271A1 (en) 2008-06-13 2011-04-06 The Timken Company Epicyclic gear system with flexpins and helical gearing
CN201381944Y (zh) * 2009-04-02 2010-01-13 杭州前进风电齿轮箱有限公司 风力发电变桨减速齿轮箱
CN201714590U (zh) * 2010-03-31 2011-01-19 南京高速齿轮制造有限公司 风力发电机用增速齿轮箱
US8491435B2 (en) * 2011-08-26 2013-07-23 General Electric Company Journal bearing for use in epicyclical gearbox and method of facilitating hydrodynamic oil flow in the journal bearing
CN103557293B (zh) * 2013-07-01 2017-03-15 陈伟 大型筒状铸造机座的软启动减速装置
JP2015043680A (ja) 2013-08-26 2015-03-05 日本電産株式会社 スピンドルモータおよびディスク駆動装置
DE102013220063A1 (de) * 2013-10-02 2015-04-02 Schaeffler Technologies Gmbh & Co. Kg Planetenradlageranordnung
CN103697059A (zh) 2013-12-09 2014-04-02 浙江大学 承受双向轴向载荷的滑动轴承
EP2933483A1 (de) * 2014-04-15 2015-10-21 Siemens Aktiengesellschaft Antriebssystem einer Windkraftanlage
CN203962939U (zh) * 2014-06-30 2014-11-26 南车戚墅堰机车车辆工艺研究所有限公司 一种风电齿轮箱的低速轴支撑结构
CN204591990U (zh) * 2015-03-18 2015-08-26 河北省轴承产业技术研究院 一种自润滑单列圆锥轴承

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020114549A1 (en) * 2001-02-21 2002-08-22 Kazuo Hokkirigawa Special type bearing device
US7662059B2 (en) 2006-10-18 2010-02-16 United Technologies Corporation Lubrication of windmilling journal bearings
US20080315697A1 (en) * 2007-06-21 2008-12-25 Laurent Bonnet Gear integrated generator for wind turbine
US8246503B2 (en) 2009-06-10 2012-08-21 United Technologies Corporation Epicyclic gear system with improved lubrication system
EP2383480A1 (de) 2010-04-30 2011-11-02 Winergy AG Planetengetriebe für eine Windkraftanlage
US20120108380A1 (en) * 2010-04-30 2012-05-03 Winergy Ag Planetary gear mechanism for a wind power plant
US8636615B2 (en) 2010-08-31 2014-01-28 Mitsubishi Heavy Industries, Co., Ltd Planetary gear train with oiling system for supplying lubricant oil to bearing of planetary gear and wind turbine generator incorporating the same
US20150125104A1 (en) * 2013-11-07 2015-05-07 Aktiebolaget Skf Bearing arrangement for fluid machinery application
DE102014205980A1 (de) 2014-03-31 2015-10-01 Schaeffler Technologies AG & Co. KG Planetentrieb mit einem Planetenrad, das mittels zwei Planetenbolzen in einem Planetenträger gelagert ist
DE102014214331A1 (de) 2014-07-23 2016-01-28 Schaeffler Technologies AG & Co. KG Planetengetriebe
EP3091255A1 (de) 2015-05-07 2016-11-09 Siemens Aktiengesellschaft Planetengetriebe
US20160327148A1 (en) * 2015-05-07 2016-11-10 Siemens Aktiengesellschaft Planetary gearbox
US20180347623A1 (en) * 2015-10-29 2018-12-06 Ntn Corporation Method for producing bearing ring, double row tapered roller bearing, and method for producing double row tapered roller bearing

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
Office Action dated Jul. 17, 2020 issued in India Patent Application No. 201937007560.
PCT International Search Report and Written Opinion of International Searching Authority dated Dec. 15, 2017 corresponding to PCT International Application No. PCT/EP2017/071140 filed Aug. 22, 2017.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10989119B2 (en) * 2018-11-23 2021-04-27 Safran Transmission Systems Planet-carrier for a mechanical reduction gear of an aircraft turbine engine
US11339869B2 (en) * 2018-11-23 2022-05-24 Safran Transmission Systems Lubricating and cooling core for a mechanical reduction gear of an aircraft turbine engine
US11644013B2 (en) 2019-05-21 2023-05-09 Miba Gleitlager Austria Gmbh Nacelle for a wind turbine

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EP3290751A1 (de) 2018-03-07
ES2814177T3 (es) 2021-03-26
CN109661531A (zh) 2019-04-19
EP3290751B1 (de) 2020-06-10
EP3507526B1 (de) 2022-07-20
EP3290751B2 (de) 2023-12-13
ES2925386T3 (es) 2022-10-17
CN109661531B (zh) 2021-12-21
ES2814177T5 (es) 2024-06-04
WO2018041671A1 (de) 2018-03-08
US20190203768A1 (en) 2019-07-04
EP3507526A1 (de) 2019-07-10

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